U.S. patent number 8,834,313 [Application Number 13/615,858] was granted by the patent office on 2014-09-16 for multiple speed transmission and method of operation.
This patent grant is currently assigned to Ford Global Technologies, LLC. The grantee listed for this patent is Reid Alan Baldwin, Gregory Daniel Goleski, Steven Gerald Thomas. Invention is credited to Reid Alan Baldwin, Gregory Daniel Goleski, Steven Gerald Thomas.
United States Patent |
8,834,313 |
Goleski , et al. |
September 16, 2014 |
Multiple speed transmission and method of operation
Abstract
A family of transmissions has four planetary gear sets, five
controllable clutches and brake, and a passive one way brake.
Selective engagement of the brakes and clutches in combinations of
three produces eight forward speed ratios and one reverse speed
ratio. The passive one way brake is engaged in the first forward
speed ratio and overruns in the second through fifth forward speed
ratios.
Inventors: |
Goleski; Gregory Daniel
(Rochester Hills, MI), Thomas; Steven Gerald (Bloomfield
Hills, MI), Baldwin; Reid Alan (Howell, MI) |
Applicant: |
Name |
City |
State |
Country |
Type |
Goleski; Gregory Daniel
Thomas; Steven Gerald
Baldwin; Reid Alan |
Rochester Hills
Bloomfield Hills
Howell |
MI
MI
MI |
US
US
US |
|
|
Assignee: |
Ford Global Technologies, LLC
(Dearborn, MI)
|
Family
ID: |
50275043 |
Appl.
No.: |
13/615,858 |
Filed: |
September 14, 2012 |
Prior Publication Data
|
|
|
|
Document
Identifier |
Publication Date |
|
US 20140080657 A1 |
Mar 20, 2014 |
|
Current U.S.
Class: |
475/292;
475/286 |
Current CPC
Class: |
F16H
3/66 (20130101); F16H 3/62 (20130101); F16H
2200/2082 (20130101); F16H 2200/2043 (20130101); F16H
2200/006 (20130101); F16H 2200/2046 (20130101); F16H
2200/2012 (20130101) |
Current International
Class: |
F16H
3/44 (20060101) |
References Cited
[Referenced By]
U.S. Patent Documents
Other References
H Benford, M. Leising, The Lever Analogy: A New Tool in
Transmission Analysis, 1982, Society of Automotive Engineers, Inc.
810102, p. 429-437. cited by applicant.
|
Primary Examiner: Bishop; Erin D
Attorney, Agent or Firm: Dottavio; James Brooks Kushman
P.C.
Claims
What is claimed is:
1. A transmission comprising: an input shaft; an output shaft; a
gearing arrangement having no more than five controllable clutches
configured to transmit power from the input shaft to the output
shaft at eight forward speed ratios and a reverse speed ratio by
selective engagement of the controllable clutches; and a passive
clutch configured to engage in a highest of the forward speed
ratios and to overrun in a second highest of the forward speed
ratios.
2. The transmission of claim 1 wherein the controllable clutches
and the passive clutch are configured to establish the speed ratios
when engaged in combinations of three.
3. The transmission of claim 1 wherein the gearing arrangement
comprises a gear element and the passive clutch is a one way brake
configured to prevent the gear element from rotation in a reverse
direction while permitting rotation in a forward direction.
4. The transmission of claim 3 wherein a first controllable clutch
of the five controllable clutches is configured to selectively hold
the gear element against rotation in the forward direction.
5. The transmission of claim 1 wherein the gearing arrangement
comprises: first, second, third, fourth, fifth, and sixth rotating
elements; a first gearing arrangement configured to fixedly
constrain the second element to rotate at a speed between speeds of
the first element and the third element and to fixedly constrain
the input shaft to rotate at a speed between speeds of the second
element and the third element; a second gearing arrangement
configured to fixedly constrain the fourth element to rotate at a
speed between speeds of the second element and the fifth element;
and a third gearing arrangement configured to fixedly constrain the
sixth element to rotate at a speed between speeds of the third
element and the output shaft.
6. The transmission of claim 5 wherein the five controllable
clutches comprise: a first brake configured to selectively hold the
fifth element against rotation; a second brake configured to
selectively hold the first element against rotation; a first clutch
configured to selectively operatively couple the fourth element to
the output shaft; a second clutch configured to selectively couple
the third element to the fifth element; and a third clutch
configured to selectively couple the fourth element to the sixth
element.
7. The transmission of claim 5 wherein the first gearing
arrangement comprises: a first simple planetary gear set having a
first sun gear as the third element, a first planet carrier fixedly
coupled to the input shaft, a first ring gear as the second
element, and a first plurality of planet gears supported for
rotation relative to the first planet carrier and in continuous
meshing engagement with both the first sun gear and the first ring
gear; and a second simple planetary gear set having a second sun
gear fixedly coupled to the first sun gear, a second planet carrier
fixedly coupled to the first ring gear, a second ring gear as the
first element, and a second plurality of planet gears supported for
rotation relative to the second planet carrier and in continuous
meshing engagement with both the second sun gear and the second
ring gear.
8. The transmission of claim 5 wherein the third gearing
arrangement comprises a third simple planetary gear set having a
third sun gear fixedly coupled to the third element, a third planet
carrier as the sixth element, a third ring gear fixedly coupled to
the output shaft, and a third plurality of planet gears supported
for rotation relative to the third planet carrier and in continuous
meshing engagement with both the third sun gear and the third ring
gear.
9. The transmission of claim 5 wherein the second gearing
arrangement comprises a double pinion planetary gear set having a
fourth sun gear fixedly coupled to the second element, a fourth
planet carrier as the fifth element, a fourth ring gear as the
fourth element, a plurality of inner planet gears supported for
rotation relative to the fourth planet carrier and in continuous
meshing engagement with the fourth sun gear, and a plurality of
outer planet gears supported for rotation relative to the fourth
planet carrier, each outer planet gear in continuous meshing
engagement with one of the inner planet gears and the fourth ring
gear.
10. The transmission of claim 1 wherein the gearing arrangement
comprises: second, third, fourth, and fifth rotating elements; a
first gearing arrangement configured to selectively constrain the
second element to rotate at a speed between zero and a speed of the
third element; a second gearing arrangement configured to fixedly
constrain the input shaft to rotate at a speed between speeds of
the second element and the third element; a third gearing
arrangement configured to fixedly constrain the fourth element to
rotate at a speed between speeds of the second element and the
fifth element; a fourth gearing arrangement configured to
selectively constrain the fourth element to rotate at a speed
between speeds of the third element and the output shaft; and
wherein the five controllable clutches comprise a first brake
configured to selectively hold the fifth element against rotation;
a first clutch configured to selectively operatively couple the
fourth element to the output shaft; and a second clutch configured
to selectively couple the third element to the fifth element.
11. The transmission of claim 10 wherein the first gearing
arrangement comprises: a simple planetary gear set having a sun
gear as the third element, a planet carrier as the second element,
a ring gear, and a plurality of planet gears supported for rotation
relative to the planet carrier and in continuous meshing engagement
with both the sun gear and the ring gear; and and wherein the five
controllable clutches further comprise a second brake configured to
selectively hold the ring gear against rotation.
12. The transmission of claim 10 wherein the fourth gearing
arrangement comprises: a simple planetary gear set having a sun
gear fixedly coupled to the third element, a planet carrier, a ring
gear fixedly coupled to the output shaft, and a plurality of planet
gears supported for rotation relative to the planet carrier and in
continuous meshing engagement with both the sun gear and the ring
gear; and and wherein the five controllable clutches further
comprise a third clutch configured to selectively couple the planet
carrier to the fourth element.
Description
TECHNICAL FIELD
This disclosure relates to the field of automatic transmissions for
motor vehicles. More particularly, the disclosure pertains to an
arrangement of gears, clutches, and the interconnections among them
in a power transmission.
BACKGROUND
Many vehicles are used over a wide range of vehicle speeds,
including both forward and reverse movement. Some types of engines,
however, are capable of operating efficiently only within a narrow
range of speeds. Consequently, transmissions capable of efficiently
transmitting power at a variety of speed ratios are frequently
employed. When the vehicle is at low speed, the transmission is
usually operated at a high speed ratio such that it multiplies the
engine torque for improved acceleration. At high vehicle speed,
operating the transmission at a low speed ratio permits an engine
speed associated with quiet, fuel efficient cruising. Typically, a
transmission has a housing mounted to the vehicle structure, an
input shaft driven by an engine crankshaft, and an output shaft
driving the vehicle wheels, often via a differential assembly which
permits the left and right wheel to rotate at slightly different
speeds as the vehicle turns.
A gearing arrangement is a collection of rotating elements and
clutches configured to impose specified speed relationships among
elements. Some speed relationships, called fixed speed
relationships, are imposed regardless of the state of any clutches.
A gearing arrangement imposing only fixed relationships is called a
fixed gearing arrangement. Other speed relationships are imposed
only when particular clutches are fully engaged. A gearing
arrangement that selectively imposes speed relationships is called
a shiftable gearing arrangement. A discrete ratio transmission has
a shiftable gearing arrangement that selectively imposes a variety
of speed ratios between an input shaft and an output shaft.
A group of elements are fixedly coupled to one another if they are
constrained to rotate as a unit in all operating conditions.
Elements may be fixedly coupled by spline connections, welding,
press fitting, machining from a common solid, or other means.
Slight variations in rotational displacement between fixedly
coupled elements can occur such as displacement due to lash or
shaft compliance. In contrast, two elements are selectively coupled
by a clutch when the clutch constrains them to rotate as a unit
whenever the clutch is fully engaged and they are free to rotate at
distinct speeds in at least some other operating condition.
Clutches include actively controlled devices such as hydraulically
or electrically actuated clutches and passive devices such as one
way clutches. A clutch that holds an element against rotation by
selectively connecting the element to the housing may be called a
brake. A group of elements are coupled if they are fixedly coupled
or selectively coupled.
The speed ratio of a shiftable gearing arrangement may be changed
by altering which clutches are engaged. An upshift occurs when the
speed ratio is decreased and a downshift occurs when the speed
ratio is increased. During a shift, a controller typically
manipulates the torque capacity of at least one controllable
clutch. When the state of more than one controllable clutch must
change during a shift event, the relative torque capacity of these
clutches must be carefully synchronized to avoid torque
disturbances that annoy vehicle occupants. Vehicle occupants are
most likely to be annoyed by torque disturbances associated with
shifts between high speed ratios because the torque disturbances
are multiplied by the gearing. The challenge of coordinating the
clutch torque capacities during a shift is avoided if either the
on-coming or off-going clutch is a passive device.
SUMMARY OF THE DISCLOSURE
A family of transmissions is disclosed. Each transmission includes
an input shaft, an output shaft, a number of rotating elements, and
gearing arrangements and clutches that impose specified fixed and
selectable speed relationships. Additionally, a method of operating
a transmission of the disclosed family is described.
In one embodiment, a transmission includes at least first, second,
third, fourth, and fifth elements in addition to the input shaft
and output shaft. A first gearing arrangement fixedly constrains
the relative speeds of the input shaft, first element, second
element, and third element. The first gearing arrangement may be,
for example, two simple planetary gear sets with the two sun gears
fixedly coupled and forming the third element, the first carrier
fixedly coupled to the input shaft, the first ring gear and second
carrier fixedly coupled and forming the second element, and the
second ring gear forming the first element. A second gearing
arrangement fixedly constrains the relative speeds of the second,
fourth, and fifth elements. The second gearing arrangement may be,
for example, a simple planetary gear set having a sun gear as the
second element, a planet carrier as the fourth element, and a ring
gear as the fifth element. Alternatively, the second gearing
arrangement may be, as another example, a double pinion planetary
gear set having a sun gear as the second element, a planet carrier
as the fifth element, and a ring gear as the fourth element. A
third gearing arrangement selectively constrains the relative
speeds of output shaft, third element, and fourth element. The
third gearing arrangement may be, for example, a simple planetary
gear set having a sun gear fixedly coupled to the third element, a
planet carrier selectively coupled to the fourth element by a
clutch, and a ring gear fixedly coupled to the output shaft.
Alternatively, the third gearing arrangement may be, as another
example, a simple planetary gear set having a sun gear fixedly
coupled to the third element, a planet carrier fixedly coupled to
the fourth element, and a ring gear selectively coupled to the
output shaft by a clutch. Alternatively, the third gearing
arrangement may be, as yet another example, a simple planetary gear
set having a sun gear selectively coupled to the third element by a
clutch, a planet carrier fixedly coupled to the fourth element, and
a ring gear fixedly coupled to the output shaft. Clutches and
brakes may selectively hold the fifth element against rotation,
selectively hold the first element against rotation, selectively
operatively couple the fourth element to the output shaft, and
selectively couple the third element to the fifth element.
In another embodiment, a transmission includes at least second,
third, fourth, and fifth elements in addition to the input shaft
and output shaft. A first gearing arrangement selectively
constrains the relative speeds of the second and third elements.
The first gearing arrangement may be, for example, a simple
planetary gear set having a sun gear as the third element, a planet
carrier as the second element, and a ring gear selectively held
against rotation by a brake. A second gearing arrangement fixedly
constrains the relative speeds of the input shaft, the second
element, and the third element. The second gearing arrangement may
be, for example, a simple planetary gear set having a sun gear as
the third element, a planet carrier fixedly couple to the input
shaft, and a ring gear as the second element. A third gearing
arrangement fixedly constrains the relative speeds of the second,
fourth, and fifth elements. A fourth gearing arrangement
selectively constrains the relative speeds of output shaft, third
element, and fourth element. Clutches and brakes may selectively
hold the fifth element against rotation, selectively operatively
couple the fourth element to the output shaft, and selectively
couple the third element to the fifth element.
In another embodiment, a transmission includes five controllable
clutches, a passive clutch, and gearing configured to establish
eight forward speed ratios and one reverse speed ratio between the
input shaft and the output shaft. The passive clutch is engaged in
the first forward speed ratio and overruns in the second forward
speed ratio. A first forward ratio is established by engaging the
first and second controllable clutch while the third, fourth, and
fifth controllable clutches remain disengaged. An upshift to a
second ratio is accomplished by engaging the third clutch while the
first and second clutches remain engaged and the fourth and fifth
clutches remain disengaged. Additional upshifts to third through
eighth forward ratios are accomplished by engaging one of the five
controllable clutches and disengaging another of the five
controllable clutches. A reverse ratio is established by engaging
the first, third, and fourth controllable clutches while the second
and fifth controllable clutches remain disengaged.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a schematic diagram of a first transmission gearing
arrangement;
FIG. 2 is a clutch application chart for the first and fourth
transmission gearing arrangements;
FIG. 3 is a schematic diagram of a second transmission gearing
arrangement;
FIG. 4 is a clutch application chart for the second transmission
gearing arrangement;
FIG. 5 is a schematic diagram of a third transmission gearing
arrangement;
FIG. 6 is a clutch application chart for the third transmission
gearing arrangement;
FIG. 7 is a schematic diagram of a fourth transmission gearing
arrangement; and
FIG. 8 is a lever diagram corresponding to the first and fourth
transmission gearing arrangements.
DETAILED DESCRIPTION
Embodiments of the present disclosure are described herein. It is
to be understood, however, that the disclosed embodiments are
merely examples and other embodiments may take various and
alternative forms. The figures are not necessarily to scale; some
features could be exaggerated or minimized to show details of
particular components. Therefore, specific structural and
functional details disclosed herein are not to be interpreted as
limiting, but merely as a representative basis for teaching one
skilled in the art to variously employ the present invention. As
those of ordinary skill in the art will understand, various
features illustrated and described with reference to any one of the
figures may be combined with features illustrated in one or more
other figures to produce embodiments that are not explicitly
illustrated or described. The combinations of features illustrated
provide representative embodiments for typical applications.
Various combinations and modifications of the features consistent
with the teachings of this disclosure, however, could be desired
for particular applications or implementations.
An example transmission is schematically illustrated in FIG. 1. The
transmission utilizes four planetary gear sets 20, 30, 40, and 50.
Gear sets 20, 30, and 50 are simple planetary gear sets. A simple
planetary gear set is a type of fixed gearing arrangement. A planet
carrier 22 rotates about a central axis and supports a set of
planet gears 24 such that the planet gears rotate with respect to
the planet carrier. External gear teeth on the planet gears mesh
with external gear teeth on a sun gear 26 and with internal gear
teeth on a ring gear 28. The sun gear and ring gear are supported
to rotate about the same axis as the carrier. A simple planetary
gear set imposes the fixed speed relationship that the speed of the
carrier is between the speed of the sun gear and the speed of the
ring gear. (This relationship is defined to include the condition
in which all three rotate at the same speed.) More specifically,
the speed of the carrier is a weighted average of the speed of the
sun gear and the speed of the ring gear with weighting factors
determined by the number of teeth on each gear.
Gear set 40 is a double pinion planetary gear set, which is another
type of fixed gearing arrangement. A planet carrier 42 rotates
about a central axis and supports an inner set of planet gears 44
and an outer set of planet gears 45. External gear teeth on each of
the inner planet gears 44 mesh with external gear teeth on a sun
gear 46 and with internal gear teeth on one of the outer planet
gears 45. External gear teeth on each of the outer planet gears 45
mesh with internal gear teeth on a ring gear 48. The sun gear and
ring gear are supported to rotate about the same axis as the
carrier. A double pinion planetary gear set imposes the fixed speed
relationship that the speed of the ring gear is between the speed
of the sun gear and the speed of the carrier. (This relationship is
defined to include the condition in which all three rotate at the
same speed.) More specifically, the speed of the ring gear is a
weighted average of the speed of the sun gear and the speed of the
carrier with weighting factors determined by the number of teeth on
each gear. Similar speed relationships are imposed by other known
types of fixed gearing arrangements.
A suggested ratio of gear teeth for each planetary gear set in FIG.
1 is listed in Table 1.
TABLE-US-00001 TABLE 1 Ring 28/Sun 26 2.73 Ring 38/Sun 36 1.50 Ring
48/Sun 46 2.80 Ring 58/Sun 56 2.29
Input shaft 10 is fixedly coupled to carrier 22. Output shaft 12 is
fixedly coupled to ring gear 58. Sun gear 26, sun gear 36, and sun
gear 56 are fixedly coupled to one another. Ring gear 28, carrier
32, and sun gear 46 are fixedly coupled to one another. Ring gear
38 is selectively held against rotation by controllable brake 62
and passively held against rotation in one direction by one way
brake 60. Carrier 42 is selectively coupled to sun gear 26, sun
gear 36, and sun gear 56 by clutch 70 and selectively held against
rotation by brake 64. Ring gear 48 is selectively coupled to
carrier 52 by clutch 66 and selectively coupled to ring gear 58 and
output shaft 12 by clutch 68.
As shown in FIG. 2, engaging the clutches and brakes in
combinations of three establishes eight forward speed ratios and
one reverse speed ratio between input shaft 10 and output shaft 12.
An X indicates that the clutch is engaged to establish the speed
ratio. When the gear sets of FIG. 1 have tooth numbers as indicated
in Table 1, the speed ratios have the values indicated in FIG. 2.
The highest forward speed ratio, which can be used to accelerate
from rest, is established by engaging controllable brake 64 and
controllable clutch 68. One way brake 60 engages passively to
transmit power in the positive direction. To upshift into the
second highest speed ratio, clutch 66 is engaged. As the torque
capacity of clutch 66 increases, the torque carried by one way
brake 60 decreases. When the torque capacity of one way brake 60
reaches zero, it overruns. An overrunning condition for a passive
clutch is characterized by relative speed between the corresponding
elements. For one way brake 60, the corresponding elements are the
transmission case 14 and ring gear 38. The remaining shifts are
accomplished by the coordinated engagement of a controllable clutch
or brake and release of a different clutch or brake as indicated in
FIG. 2.
Another example transmission is illustrated in FIG. 3. The
transmission utilizes three simple planetary gear sets 20, 30, and
50 and one double pinion planetary gear set 40. A suggested ratio
of gear teeth for each planetary gear set is listed in Table 1
above. Input shaft 10 is fixedly coupled to carrier 22. Sun gear
26, sun gear 36, and sun gear 56 are fixedly coupled to one
another. Ring gear 28, carrier 32, and sun gear 46 are fixedly
coupled to one another. Ring gear 48 is fixedly coupled to carrier
52. Ring gear 38 is selectively held against rotation by
controllable brake 62 and passively held against rotation in one
direction by one way brake 60. Carrier 42 is selectively coupled to
sun gear 26, sun gear 36, and sun gear 56 by clutch 70 and
selectively held against rotation by brake 64. Output shaft 12 is
selectively coupled to ring gear 58 by clutch 72 and selectively
coupled to ring gear 48 and carrier 52 by clutch 68. As shown in
FIG. 4, engaging the clutches and brakes in combinations of three
establishes eight forward speed ratios and one reverse speed ratio
between input shaft 10 and output shaft 12.
A third example transmission is illustrated in FIG. 5. The
transmission utilizes three simple planetary gear sets 20, 30, and
50 and one double pinion planetary gear set 40. A suggested ratio
of gear teeth for each planetary gear set is listed in Table 1
above. Input shaft 10 is fixedly coupled to carrier 22. Output
shaft 12 is fixedly coupled to ring gear 58. Sun gear 26 is fixedly
coupled to sun gear 36. Ring gear 28, carrier 32, and sun gear 46
are fixedly coupled to one another. Ring gear 48 is fixedly coupled
to carrier 52. Ring gear 38 is selectively held against rotation by
controllable brake 62 and passively held against rotation in one
direction by one way brake 60. Carrier 42 is selectively held
against rotation by brake 64. Sun gear 26 and sun gear 36 are
selectively coupled to carrier 42 by clutch 70 and selectively
coupled to sun gear 56 by clutch 74. Output shaft 12 and ring gear
58 are selectively coupled to ring gear 48 and carrier 52 by clutch
68. Note that engaging clutch 68 forces gear set 50 to rotate as a
unit. Clutch 68 could alternatively accomplish this function by
selectively coupling any two of the elements of gear set 50. As
shown in FIG. 6, engaging the clutches and brakes in combinations
of three establishes eight forward speed ratios and one reverse
speed ratio between input shaft 10 and output shaft 12.
A fourth example transmission is illustrated in FIG. 7. The
transmission utilizes four simple planetary gear sets 20, 30, 80,
and 50. The planet gears 84 of gear set 80 are wide enough to mesh
with two ring gears 88 and 90. Although ring gear 88 and ring gear
90 are not directly connected, they are forced to rotate at the
same speed by the interaction with planet gear 84. The carrier 82
of gear set 80 extends outwardly between ring gears 88 and 90 in
the circumferential space between the planet gears 84. A suggested
ratio of gear teeth for each planetary gear set is listed in Table
2.
TABLE-US-00002 TABLE 2 Ring 28/Sun 26 2.73 Ring 38/Sun 36 1.50 Ring
48/Sun 46 1.80 Ring 58/Sun 56 2.29
Input shaft 10 is fixedly coupled to carrier 22. Output shaft 12 is
fixedly coupled to ring gear 58. Sun gear 26, sun gear 36, and sun
gear 56 are fixedly coupled to one another. Ring gear 28, carrier
32, and sun gear 86 are fixedly coupled to one another. Ring gear
38 is selectively held against rotation by controllable brake 62
and passively held against rotation in one direction by one way
brake 60. Ring gear 90 is selectively coupled to sun gear 26, sun
gear 36, and sun gear 56 by clutch 70. Ring gear 88 is selectively
held against rotation by brake 64. Carrier 82 is selectively
coupled to carrier 52 by clutch 66 and selectively coupled to ring
gear 58 and output shaft 12 by clutch 68. As shown in FIG. 2,
engaging the clutches and brakes in combinations of three
establishes eight forward speed ratios and one reverse speed ratio
between input shaft 10 and output shaft 12.
FIG. 8 describes the transmissions of FIGS. 1 and 7 in the form of
a lever diagram. Gear elements which rotate about a common axis and
have speeds with a fixed linear relationship are shown along a
lever according to their relative speeds. The two elements that
have the most extreme speeds are shown at the endpoints of the
lever. The remaining elements are shown at intermediate points
according to the weighting factors. Four node lever 92 corresponds
to gear sets 20 and 30 with ring gear 38 as the 1st element, ring
gear 28 and carrier 32 as the 2nd element, and sun gears 26 and 36
as the 3rd element. The 1st and 3rd elements will have the most
extreme speeds among the four elements in all operating conditions.
The input and 2nd element will have intermediate speeds with the
speed of the 2nd element closer to that of the 1st element and the
speed of the input closer to that of the 3rd element. Many known
fixed gearing arrangements impose the speed relationship
represented by a four node lever. Specifically, any two simple or
double pinion planetary gear sets with two fixed connections can be
represented by a four node lever. Also, the speed relationship may
be implemented by arrangements with shared planet gears or stepped
planet gears. Gear sets 20 and 30 may be replaced with another
fixed gearing arrangement that imposes the same speed relationships
without impacting the operation or resulting speed ratios. Some of
these gearing arrangements will be preferable to others in terms of
packaging, efficiency, and planet gear speeds. Similarly, lever 94
corresponds to either gear set 40 of FIG. 1 or gear set 80 of FIG.
7. In FIG. 1, sun gear 46 is the 2nd element, ring gear 48 is the
4th element, and carrier 42 is the 5th element. In FIG. 7, sun gear
86 is the 2nd element, carrier 82 is the 4th element, and ring
gears 88 and 90 are the 5th element. Finally, lever 96 corresponds
to gear set 50, with the 3rd element corresponding to sun gear 56,
the 6th element corresponding to carrier 52.
While exemplary embodiments are described above, it is not intended
that these embodiments describe all possible forms encompassed by
the claims. The words used in the specification are words of
description rather than limitation, and it is understood that
various changes may be made without departing from the spirit and
scope of the disclosure. As previously described, the features of
various embodiments may be combined to form further embodiments of
the invention that may not be explicitly described or illustrated.
While various embodiments could have been described as providing
advantages or being preferred over other embodiments or prior art
implementations with respect to one or more desired
characteristics, those of ordinary skill in the art recognize that
one or more features or characteristics can be compromised to
achieve desired overall system attributes, which depend on the
specific application and implementation. These attributes may
include, but are not limited to cost, strength, durability, life
cycle cost, marketability, appearance, packaging, size,
serviceability, weight, manufacturability, ease of assembly, etc.
As such, embodiments described as less desirable than other
embodiments or prior art implementations with respect to one or
more characteristics are not outside the scope of the disclosure
and can be desirable for particular applications.
* * * * *